Combination break-away service valve assembly



NOV. 1, 1966 CASTELLO 3,282,292

COMBINATION BREAK-AWAY SERVICE VALVE ASSEMBLY Filed Aug. 24, 1965 5 sheets-Sheet 1 J 2 ii 0% 625612110 Nov. 1, 1966 A. M. CASTELLO 3,282,292

COMBINATION BREAK-AWAY SERVICE VALVE ASSEMBLY Filed Aug. 24, 1965 8 Sheets-Sheet 2 ar/m: Jnfiozzy/M 621566.00

COMBINATION BREAK-AWAY SERVICE VALVE ASSEMBLY Filed Aug. 24, 1965 5 Sheets-Sheet 5 gall 1N VENTOR:

United States Patent 3,282,292 CGMBINATIQN BREAK-AWAY SERVICE VALVE ASSEMBLY Anthony M. Castello, Wichita, Kan s., assignor to The Coleman Company, Inc, Wichita, KilllS-, a corporation of Kansas Filed Aug. 24, 1965, Ser. No. 482,139

Claims. (Cl. 137614.15)

This invention relates to a combination break-away and service valve assembly means for use in connection with the installation and repair of refrigeration systems. The present application is a continuation-in-part of my copending application, Serial No. 237,180, filed November 13, 1962, which was a continuation-in-part of copending application, Serial No. 164,036, filed January 3, 1962, both of which are now abandoned.

When installing air conditioning systems in residences and the like it is sometimes desirable because of the na ture of the buildings construction or because of other considerations to install the evaporator coil and fan indoors and then proceed to install the compressor and condensor section of the air conditioner outdoors, thereafter joining the components of the air conditioner with suitable tubing. At other times, the construction of the building permits or even necessitates that the entire air conditioner be installed as a self-contained unit. It also frequently occurs that the difliculty of repair of an air conditioner would be greatly reduced if the defective section could be detached and taken to a repair shop without disturbing the other sections of the machine and without losing the refrigerant charge in such other sections.

Spring-loaded valves have been known in the past for sealing off each of two sections of a pressure fluid system as those sections are disconnected or are readied for disconnection, but such valves are generally unsatisfactory because of their tendency to leak in operation having only spring tension to depend upon and because of their relatively complex and expensive construction. Accordingly, it is a main object of the present invention to provide relatively low-cost and fool proof, positively-actuated, valve means for insertion in the refrigerant transfer conduit of a refrigeration system that will permit the connection and disconnection of the componetnts of the system, without loss of the refrigerant charge in either section, and without introducing air or moisture into the refrigeration fluid.

It is also desirable to provide a valve means which when fully opened provides a minimum pressure drop through the valve assembly. It is therefore an object to provide a valve assembly which accomplishes this result, the valve members being moveable from their closed positions to positions where they impose little or no restriction on the flow of refrigerant fluid.

In refrigerant systems of the character described, it is usually necessary or at least highly desirable to provide a service valve, which may be utilized to introduce or remove refrigerant fluid from the system. If the system contains an overcharge of fluid, or the fluid is contaminated with air or moisture, removal of part or all of the fluid may be required. More frequently, however, it is necessary to add some refrigerant fluid to the system, since small losses of refrigerant during extended periods of operations are almost unavoidable. Heretofore, a service valve has been provided as a separate and independent valve. It is therefore an object of this invention to provide a combination break-away and service valve assembly, which performs the functions of a break-away valve as described above, and at the same time provides the functions of a service valve, thereby providing a less expensive and more efiicient construction than has heretofore been known.

Other objects will appear from the specification and drawings in which:

FIGURE 1 is a broken side elevational view of a break-away and service valve assembly embodying the present invention, the valve being shown partly in section;

FIGURE 2 is an elevational and partly sectional view similar to FIGURE 1 but showing the parts in different positions of adjustment;

FIGURE 3 is a cross sectional view taken along line 33 of FIGURE 2;

FIGURE 4 is an exploded side elevational view showing the separated sections of the break-away valve prior to capping and plugging of those sections;

FIGURE 5 is an enlarged cross sectional view taken along line 5-5 of FIGURE 2;

FIGURE 6 is a broken side elevational view, taken partly in section, illustrating a break-away and service valve assembly comprising a second embodiment of the present invention;

FIGURE 7 is an elevational view, taken partly in section, illustrating the valve of the second embodiment in closed condition;

FIGURE 8 is an enlarged cross sectional view taken along line 8-8 of FIGURE 6;

FIGURE 9 is an enlar-gedcross sectional view taken along line 99 of FIGURE 6;

FIGURE 10 is an exploded side elevation view of the separated sections of the valve of the second embodiment;

FIGURE 11 is a broken side elevational view, partly in section, illustrating a third embodiment of a breakaway and service valve assembly construction in accordance with the present invention;

FIGURE 12 is an enlarged fragmentary side elevational view, partly in section, of the valve means of FIG. 11 which also provides the service valve, the service valve being shown in closed position; and

FIGURE 13 is enlarged fragmentary side elevational view, partly in section, a side sectional, of a portion of the assembly of FIGURE 11, showing the two line valves in closed position and the service valve in open position.

In the embodiment of the invention illustrated in FIG- URES 1 through 5 of the drawings, the numeral 10 generally designates a break-away valve comprising a valve casing 11 which has a pair of axially aligned casing sections 12 and 13. In the illustration given, section 12 is formed from two coaxial tubular parts 14 and 15 which are telescoped and permanently secured at their ends with a partition 16 disposed therebetween. Section 13 is similarly formed by two generally tubular pieces 17 and 18 which are permanently secured together in axial alignment. Casing section 13 provides an outer portion 13a, an intermediate portion 130, and an inner portion 13d.

Section 12 may constitute the inlet section of the valve casing and is provided with an axially-disposed inlet opening 19 at one end thereof. The end opening is internally threaded for connection to a feed tube or pipe 20 of a pressure fluid system.

The other section 13 may constitute an outlet section and is provided with a lateral outlet port 21 in the side wall thereof, or more specifically in intermediate section 130. Port 21 defines a laterally-extending flow passage for connection to one end of a refrigerant transfer conduit, while opening 19 defines an axial-extending passage for connection to the other end of the refrigerant transfer conduit. An internally threaded sleeve 22 is fixed to the outlet section for placing that section in communication with a suitable outlet tube or pipe 23. It is to be noted that, unlike inlet opening 19, the outlet opening 21 and the passage of the outlet sleeve 22 are not coaxial with the sections of the valve casing.

The two sections 12 and 13 are detachably connected by releasable coupling means comprising an internally threaded union ring or coupling 24 thereby providing a break-away joint. The annular coupling is rotatably carried by the fianged end piece 18 of section 13 and threadedly receives the threaded end portion 25 of easing section 12. As shown in FIGURE 2, a compression ring 26 is clamped between the opposing end faces of the two sections for sealingly connecting those sections.

Each of the sections 12 and 13 contains a valve seat and an axially-movable valve member. More specifically, the inner portions of the sections provide valve seats on each side of and adjacent to the break-away joint. In outlet section 13, the valve seat is located in inner portion 13d and comprises an inward axial extension 27 of the end piece 18 and the valve member 28 is provided with a frusto-conical surface 2% for sealingly engaging the annular seat. In casing section 12 the valve seat comprises a cylindrical bore 30 through end portion 25 and the valve member 31 is in the form of a cylindrical plunger equipped with a resilient sealing ring 32 carried within an annular groove. As shown most clearly in FIGURES 1 and 2, the two valve members 28 and 31 are aligned for movement along the longitudinal axis of the elongated valve casing.

The means for simultaneously shifting both valve members axially into seated or unseated positions comprises a pair of axially-aligned threaded shafts 33 and 34. In the illustration given, these shafts are integral with valve members 28 and 31, respectively. Shaft 33 extends outwardly and axially away from valve seat 27 and is threadedly received within a threaded passage or opening 35 in the outer portion 13a of easing section 13. The shaft 33 projects through the casing section 13a and is provided with an externally projecting end portion 36 of non-circular cross section which may be gripped by a suitable tool for rotation of the threaded shaft. If desired, a protective cover 37 (FIGURE 1) may be threadedly fitted upon the casing section 13 to conceal and protect the projecting end 36 of the shaft.

Like shaft 33, shaft 34 projects outwardly and axially from the valve seat 30. In FIGURES 1 and 2 it will be observed that the externally threaded shaft is threadedly received within a central opening 38 in partition or septum 16. In addition, shaft 34 has a longitudinal bore 39 extending therethrough, the bore being closed by a plug 41 at the shafts outer end. Bore 39 not only extends through the shaft but also continues into and through the valve member 31 which is integral with that shaft. At the valve members innermost end, the bore 39 is slightly constricted and defines an opening 41 of non-circular cross section.

Opening 41 has the same cross-sectional configuration as connecting shaft 42 and slidably receives that shaft, which comprises drive shaft means interconnecting valves 28 and 31 for simultaneously opening and closing the valves by ap lying rotational movement to one of the valves, preferably, the conical valve 28 is driven directly through stem 33 and the cylindrical valve 31 is driven through shaft 42, as shown. Referring to FIGURE 5, it will be noted that shaft 42 is hexagonal in shape although it is to be understood that other non-circular cross sectional configurations might be used. The end of the shaft 42 received within the bore of shaft 34 is provided with an enlarged head 43 and a compression spring 44- is disposed within the bore between the head and plug 40. The opposite end portion of the connecting shaft 42 projects axially beyond the cylindrical valve member 31 and is releasably received within a hexagonal socket 4 in valve member 28 (FIGURE 5). Thus, the non-circular shaft 42 connects valve shafts 33 and 34 for simultaneous rotation, such rotation being imparted to both shafts and valve members by means of a wrench or other suitable tool applied to the exposed ends 36 of shaft 33.

Since shafts 33 and 34 are threadedly connected to the sections of the valve casing in which they are mounted, rotation of those shafts will also produce axial displacement thereof. As shown in FIGURES 1 and 2, the two valve shafts are reversely threaded, one being provided with a left hand thread and the other with a right hand thread, and therefore, as these shafts are rotated in the same direction they migrate axially in opposite directions. If desired, shaft 33 may be provided with more threads per inch than shaft 34 to provide greater axial movement of cylindrical valve 31 per rotation.

Partition 1% is illustrated in FIGURE 3 as being noncircular in shape and, as a result, this partition provides a secure threaded mounting for valve shaft 34 without at the same time preventing the flow of pressure fluid through casing section 12. In the illustration given, the partition is provided with arcuate peripheral cutouts 46 which define the openings for the flow of fluid.

Valve section 13, or more specifically outer portion 13a, is provided with a suitable nipple 47 protected by a removable threaded cap 48. The nipple 47 has an internal passage 47a which communicates with a service port 475 that in turn communcates with an interior passage 13b. At the inner end of passage 13b there is provided a valve seat 2712, which cooperates with conical surface 29b of valve 28 to close passage 13b, as shown in FIG- URE 1. Passage 13b is shown in open position in FIG- URE 2. The purpose af this construction is subsequently explained in greater detail.

A protective cap 4 9 and a plug 50, along with sealing rings 51 and 52, may also be provided for covering and plugging the ends of valve sections 12 and 13, respectively, when the valve is divided or broken apart.

In the operation of the structure already described, conduits 2t and 23 would normally communicate with different sections of a pressure fluid system such as, for example, the evaporator and the compressor-condenser sections of an air conditioner. If an operator should desire to separate the evaporator and condenser sides of the air conditioner, he need merely to remove cover 37 and rotate the end 36 of valve shaft 33. Upon rotation in a counterclockwise direction (as viewed in FIGURE 5) shaft 33 and valve 28 will move axially inwardly from the open position of FIGURE 1 into the seated position of FIGURE 2. At the same time, shaft 34 and valve member 31 will move axially inwardly in the opposite direction so that the cylindrical valve member is shifted into the cylindrical valve seat or passage as shown in FIG- URE 2. In this manner, both of the casing sections 12 and 13 are separately and simultaneously sealed against the flow of pressure fluid therethrough. When the valves are fully seated as shown in FIGURE 2, the operator simply unthreads the coupling ring 24 and connects cover 4-9 and plug 50' to the separated sections. Assembly of the disconnected sections is achieved by simply reversing the foregoing procedure.

It will be noted that since valve seat 30 is cylindrical in shapt, an effective sealing action will occur in section 12 in any position of valve member 31 in which its sealing ring 32 is in contact with the seat. The parts of the valve are proportioned and arranged so that when valve shaft 33 is turned inwardly to force valve member 28 against annular seat 27, the sealing ring of cylindrical valve member 31 will be located at some point along the axial extent of cylindrical valve seat 30. Effective sealing action between the valve member 31 and its cylindrical seat 31 will therefore occur regardless of slight differences in the axial position of seated valve 28 resulting from wear, compression, or any other causes. It will be noted that valve 28 functions as a double acting valve seating against valve seat 27a in its inner position and against valve seat 27b in its outer position. This permits the unit to be employed as a combination break-away and service valve. For example, when it is desired to introduce or remove refrigerant fluid, valve 28 is moved to its back seated position, as shown in FIGURE 1, where it closes passage 13d. Cap 48 is then removed, and a suitable conduit connected to nipple 47 for introduction or removal of the refrigerant fluid. Valve 28 is then moved to an inner position where passage 13b communicates with the interior of intermediate portion 130, and also, with the lateral port 21. If desired, valve 28 may be moved to its innermost seated position, shown in FIG- URE 2, thereby fully opening the port 21 to passage 13b and to port 47b. Alternatively, valve 28 may be positioned intermediately between the valve seats 27a and 27b, thereby placing port 4712 in communication with conduit 20 as well as with the conduit 23. When it is desired to disconnect the refrigerant service line, valve 28 is moved to its outer seated position closing passage 13b. The refrigerant service line is dis-connected from nipple 27, and cap 48 is replaced. Thereafter, the valve assembly can be used as a break-away valve, or at another time as -a service valve.

In the embodiment illustrated in FIGURES 6 through 10 corresponding parts have the same numbers except that the numbers are primed. The construction is very similar to the structure already described, except that the connecting shaft 42 is permanently aflixed to rotatable shaft 33. The connecting shaft is of hexagonal or otherwise non-circular cross-section, and has its opposite end slidably received within the bore of threaded shaft 34 and of the valve member 31 integral with that shaft. Unlike connecting shaft 42, shaft 42 is not provided with an enlarged head at its free end but is instead of substantially uniform cross-sectional dimensions throughout its entire longitudinal extent. The bore of threaded shaft 34', or at least the opening 41' thereof, has the same cross-sectional configuration as the connecting shaft 42' and since the connecting shaft is received within that bore, the three shafts 34, 42', and 33 are locked against independent relative rotation.

Shaft 42' may of course be withdrawn from the socket or bore 41' of the threaded shaft 34' when the two sections 12 and 13' are separated (FIGURE 10). The connecting shaft 42', being permanently connected to shaft 33', remains with section 13 when the two sections are separated. In the operation of this embodiment, when the two sections are connected together, rotation of the end 36 of valve shaft 33' in a counterclockwise direction (as viewed in FIGURE 9) will result in movement of valve 28 in an axial direction towards its seat 27. At the same time, shaft 34' and its valve member 31 will move axially inwardly in the opposite direction into sealing contact with the cylindrical valve seat 30', the slidable relationship of the connecting shaft 42' and the socket-providing valve member 31 and shaft 34 allowing such axial movement of the parts without permitting independent relative rotation thereof.

When the valves are fully seated (FIGURE 7), the operator simply unthreads the coupling ring 24' and, if desired, connects a suitable cover and plug to the separated sections. Assembly of the disconnected sections is achieved by simply reversing this procedure.

In the embodiment shown in FIGURES 11 to 13, corresponding parts are given the same numbers, except that the numbers are. double primed. The construction is generally similar to the embodiments previously described.

The cylindrical valve 31" is provided at its inner end with a pilot portion 31a" of reduced diameter, which directs and guides the valve into casing section 14" and through sealing ring 32". The sealing ring 32" is seated in recess 32a" at the inner end of casing section 14" adjacent the break-away joint. The ring 32" is held in place by a retainer ring 26a" which also assists in maintaining the sealing ring 26". When valve 31 is moved from its open position as shown in FIGURE 11, to its closed position as shown in FIGURE 13, pilot portion 31a" passes through ring 32 and into the inner portion 13b" of easing section 13", thereby substantially filling the space within inner portion 13d" up to valve seat 27a", as shown in FIGURE 13. A small clearance is provided between the inner end of pilot portion 31a" and the inner end of portion 29a" of conical valve 28 so that valve 28 can be driven into tight seating engagement with seat 27a". It will be apparent that the cylindrical valve 31" has a range of seating positions. Whenever the enlarged rearward portion of the valve is within the ring 32", a seal is provided.

In the illustration given, the valve seat 2712" is provided with a short conical surface for cooperating with conical surface of the valve portion 29b to close the passage 13b". In FIGURE 13, the nipple 47" is shown with the cap 48" in place. It is to be understood that a refrigerant service line would be connected to the nipple and that the refrigerant fluid could thereby be introduced through the port 47/)" and passed through the lateral port 21", as illustrated by the arrows in FIGURE 13, thereby introducing additional refrigerant to the system.

It will be apparent from an examination of the embodiment of FIGURES l and 2 as well as the embodiment of FIGURES 6 and 7, that the cylindrical valve 31, 31' move a greater distance away from their co-acting. seats than the conical valves 28, 28'. This feature is illustrated more'particularly in FIGURE 11. The approximate distance of movement of the cylindrical valve 31" from fully opened position to seated position is indicated by the bracket a, while the corresponding movement of the conical valve 28" is indicated by the bracket b. It has been found desirable to make the movement of the cylindrical valve from 2 to 3 times that of the movement of the conical valve. This can readily be accomplished by providing from 2 to 3 times as many threads per inch on shaft 33" (and for the threads cooperating therewith) as on stem 34". By using a double or triple pitch thread on stem 34" compared with a single pitch thread on stem 33", the cylindrical valve 31" may be moved from within the section of restricted diameter of seating section 30" to the portion of enlarged diameter 14a", while conical valve 28" moves the shorter distance from valve seat 27a" to valve seat 27b.

It will also be noted that the valve 28 in its outermost position while contacting valve seat 27b" is at the outside of port 21", thereby providing a minimum restriction of the flow passage provided by port 21". Similarly, the valve 31" in its outermost position provides relatively little restriction in the flow passage 14a". Since the force or torque required to move valve 31" from open to seated position is relatively small, the inner connecting drive shaft means 42" can be of relatively small diameter, thereby providing little restriction in the portions of the sections 14" and 13" through which it extends.

In the closed positions of the line valves, as shown in FIGURES 2, 7, and 13, it is preferred to have a minimtlm of space between the adjacent ends of the conical and cylindrical valves. When the break-away joint is opened, there will be little loss of refrigerant fluid, and when the joint is reconnected, there will be little introduction of air or moisture.

While in the foregoing I have disclosed several embodiments of the present invention in considerable detail for purposes of illustration, it will be understood by those skilled in the art that many of these details may be varied without departing from the spirit and scope of the invention.

I claim:

1. Combination break-away and service valve assembly for insertion in the refrigerant transfer conduit of a refrigeration system, comprising a pair of hollow casing sections arranged in axial alignment, releasable coupling means sealingly connecting the adjacent ends of said sections to provide a break-away joint, the inner portions of eachof said sections internally providing a valve seat adjacent said joint on one side thereof, rotatable valve means mounted within each of said sections for movement respectively into and out of engagement with the seat provided by its section, drive shaft means interconnecting said valve means for simultaneously opening and closing said valve means by applying rotational movement to one of said valve means, one of said casing sections having an intermediate portion outwardly of the valve seat therein providing a lateral port in the side wall thereof defining a laterally-extending flow passage for connection to one end of said transfer conduit, the outer end of the other of said casing sections being connectable to the other end of said transfer conduit, said one casing section also having an outer portion providing a service port communicating with the interior thereof, a removable closure for said service port, a valve seat provided within said one casing section between said service port and said lateral port, the said valve means in said one casing section being a double acting valve seating agains said last-mentioned valve seat in its outer position and against the first-mentioned valve of said one casing section in its inner position, and means for rotating said lastmentioned valve means extending through said casing outer portion and externally thereof, said valve means in the other of said casing sections being a cylindrical valve having an axial range of seating positions with respect to the said seat provided for coaction therewith, said cylindrical valve being driven by said drive shaft means.

2. The combination of claim 1 wherein the said do-uble acting valve in said one casing section provides two conical portions, one facing toward each of the said valve seats in said one section for respective coaction therewith.

3. The combination of claim 2 wherein separate threaded means are provided for moving each of said valve means, said cylindrical valve being movable further way from its coacting seat than the simultaneous movement of said conical valve.

4. The combination of claim 2 wherein said conical and cylindrical valves provide closely spaced inner end portions when said valves are in their innermost seated positions.

5, The combination of claim 6 wherein said double acting valve is movable to :an open position adjacent the outer side of said lateral port.

References Cited by the Examiner UNITED STATES PATENTS 752,220 2/1904 Halley et a1. 137614.15 875,496 12/1907 Bishop 137614.15 1,703,311 2/1929 Little 137614.12 X 2,934,915 5/1960 Morse 137-614 X 2,995,337 8/1961 Tanner 251324 V WILLIAM F. ODEA, Primary Examiner.

ISADOR WEIL, D. LAMBERT, Examiners. 

1. COMBINATION BREAK-AWAY AND SERVICE VALVE ASSEMBLY FOR INSERTION IN THE REFRIGERANT TRANSFER CONDUIT OF A REFRIGERATION SYSTEM, COMPRISING A PAIR OF HOLLOW CASING SECTIONS ARRANGED IN AXIAL ALIGNMENT, RELEASABLE COUPLING MEANS SEALINGLY CONNECTING THE ADJACENT ENDS OF SAID SECTIONS TO PROVIDE A BREAK-AWAY JOINT, THE INNER PORTIONS OF EACH OF SAID SECTIONS INTERNALLY PROVIDING A VALVE SEAT ADJACENT SAID JOINT ON ONE SIDE THEREOF, ROTATABLE VALVE MEANS MOUNTED WITHIN EACH OF SAID SECTIONS FOR MOVEMENT RESPECTIVELY INTO AND OUT OF ENGAGEMENT WITH THE SEAT PROVIDED BY ITS SECTION, DRIVE SHAFT MEANS INTERCONNECTING SAID VALVE MEANS FOR SIMULTANEOUSLY OPENING AND CLOSING SAID VALVE MEANS BY APPLYING ROTATIONAL MOVEMENT TO ONE OF SAID VALVE MEANS, ONE OF SAID CASING SECTIONS HAVING AN INTERMEDIATE PORTION OUTWARDLY OF THE VALVE SEAT THEREIN PROVIDING A LATERAL PORT IN THE SIDE WALL THEREOF DEFINING A LATERALLY-EXTENDING FLOW PASSAGE FOR CONNECTION TO ONE END OF SAID TRANSFER CONDUIT, THE OUTER END OF THE OTHER OF SAID CASING SECTIONS BEING CONNECTABLE 